EP0940592B1 - Kombiniertes Lager - Google Patents

Kombiniertes Lager Download PDF

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Publication number
EP0940592B1
EP0940592B1 EP99301563A EP99301563A EP0940592B1 EP 0940592 B1 EP0940592 B1 EP 0940592B1 EP 99301563 A EP99301563 A EP 99301563A EP 99301563 A EP99301563 A EP 99301563A EP 0940592 B1 EP0940592 B1 EP 0940592B1
Authority
EP
European Patent Office
Prior art keywords
bearing
outer ring
ball
inner ring
ring
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP99301563A
Other languages
English (en)
French (fr)
Other versions
EP0940592A1 (de
Inventor
Rikuro c/o Minebea Co. Ltd. Obara
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Minebea Co Ltd
Original Assignee
Minebea Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Minebea Co Ltd filed Critical Minebea Co Ltd
Publication of EP0940592A1 publication Critical patent/EP0940592A1/de
Application granted granted Critical
Publication of EP0940592B1 publication Critical patent/EP0940592B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C39/00—Relieving load on bearings
    • F16C39/02—Relieving load on bearings using mechanical means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/52—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions
    • F16C19/522—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions related to load on the bearing, e.g. bearings with load sensors or means to protect the bearing against overload
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C21/00—Combinations of sliding-contact bearings with ball or roller bearings, for exclusively rotary movement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/103—Construction relative to lubrication with liquid, e.g. oil, as lubricant retained in or near the bearing
    • F16C33/104—Construction relative to lubrication with liquid, e.g. oil, as lubricant retained in or near the bearing in a porous body, e.g. oil impregnated sintered sleeve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/583—Details of specific parts of races
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
    • F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2370/00—Apparatus relating to physics, e.g. instruments
    • F16C2370/12—Hard disk drives or the like

Definitions

  • the present invention relates to a composite bearing structure and more particularly to a composite bearing structure composed of a combination of single row ball bearings and cylindrical bearings.
  • FIG 17 shows a sectional view through a single row ball bearing.
  • the outer ring 101 freely inclines through an angle of ⁇ on top of ball 102.
  • a rotating body such as the hub of a spindle motor is mounted on outer ring 101, this rotating body will vibrate in both the axial and radial directions with relation to inner ring 103, and so the rotation will be unstable.
  • two single row ball bearings 100 and 110 are fixed together in a parallel assembly, or, as shown in FIG 19, to further reduce the rotational vibration, a spacer 120 is mounted between the two single row ball bearings 100 and 110, increasing the space between ball bearing 100 and ball bearing 110, preventing rotational vibration and achieving stable high precision rotation.
  • the present invention has been acomplished in view of the above-mentioned problems and it is an object of the invention to provide a bearing struture in which a single ball bearing is used in such a way as to prevent rotational vibration in the same way as if two ball bearing were used, and in addition to provide a low cost, thin type ball bearing structure.
  • FR-A-1464889 discloses a hydrodynamic needle or ball bearing. comprising the features of the preamble of claim 1.
  • GB-A-1042549 discloses a needle bearing.
  • a composite bearing having a single row ball bearing and cylindrical bearing comprising:
  • the present invention provides a structure using one single row ball bearing (the smallest unit which can be used in a ball bearing), which, in order to solve the problem of inclination and vibration in the inner and outer rings, uses a sintered, oil-impregnated bearing or alternatively, a non-oil-impregnated dry bearing, a fluid bearing, etc.(There are defined with a friction bearing.) where an inner or an outer ring of the friction bearing is mounted either on one side or on both sides, in a structure which reduces inclined rotation.
  • the radial load is mainly received by the ball, and when the inner and outer rings are about to vibrate and incline, a sintered, oil-impregnated bearing mounted either on one side or on both sides of the inner ring or outer ring closes the gap and slightly contacts the opposing inner or outer ring thus reducing the inclination, said contact surface being, because it is the inner or outer ring surface of the single row ball bearing, a very precisely finished surface, and thus the frictional loss from the inclination load is slight.
  • the thrust load is all received by the ball.
  • the thrust load is also all received by the ball, and the friction loss received by the inclination-reducing sintered, oil-impregnated bearing is very slight, and therefore there is no great influence on either the rotational precision or the lifetime reliability.
  • the present invention makes possible a bearing with minimal width, which can be formed by a composite bearing having an anti-collapse function, and which does not require much increase of the width of the single row ball bearing.
  • a single composite bearing comprising an inner ring 1, having a width L of the size necessary to restrain the inclination of the axis within the permitted range, and an outer ring 2, having a width which is half the width of the above mentioned width L, which is mounted above the outside half of inner ring 1 and separated from inner ring 1 by a gap.
  • a ball 3 is fitted into this gap between the rings and rests in grooves made in each ring. The ball 3 is prevented from escaping from the groove by retainer 5.
  • Inner ring 1 has an external form which is superfinished to high precision in one piece and contains the ball groove described above.
  • the outside of outer ring 2 is press fitted into outer ring sleeve 6, which is made of metal having a cylindrical form of width L.
  • Cylindrically-shaped sintered, oil-impregnated bearing 4 is press fitted into the space formed by the inner parts of outer ring 2, ball 3 and retainer 5.
  • the outer diameter of this sintered, oil-impregnated bearing 4 is the same as the inner diameter of outer ring sleeve 6, and its inner diameter is slightly larger than the outer diameter of inner ring 1. Because of this, sintered, oil-impregnated bearing 4 is press fitted firmly to the inner side of outer ring sleeve 6 and forms a small gap g above the peripheral face of inner ring 1.
  • This inclination suppression gap g in order to prevent the inclination from exceeding the permitted range, is determined by the dimensions A and B shown in FIG 1, and accordingly extremely high precision processing is required.
  • FIGS 3, 5 and 7 show basically similar structures to the above, in which a single composite bearing has an inclination suppression gap g formed on the inner ring 1 side. These structures will be described in detail below.
  • a single composite bearing shown in FIG 3 has a structure in which the single composite bearing and the inclination suppression gap g are established on the inner ring 1 side.
  • Sintered, oil-impregnated bearing 4 processed to the dimensions outer diameter C, inner diameter B and width W, is combined with a single row ball bearing formed by inner ring 1, outer ring 2, ball 3 and retainer 5.
  • This embodiment does not require the outer ring sleeve 6 of the embodiment shown in FIG 1, and instead the parts can directly assembled together.
  • This embodiment has the advantage of allowing the diametrical dimension to be reduced.
  • a single composite bearing shown in FIG 5 has a structure in which the single composite bearing and the inclination suppression gap g are established on the inner ring 1 side.
  • Sintered, oil-impregnated bearing 4 is combined with a single row ball bearing formed by inner ring 1, outer ring 2, ball 3 and retainer 5.
  • outer ring 2 has a stepped large diameter part F, and sintered, oil-impregnated bearing 4 is press fitted or bonded onto this stepped large diameter part F of outer ring 2 to form a structure which, together with inner ring 1, maintains inclination suppression gap g.
  • sintered, oil-impregnated bearing 4 is fixed together with outer ring 2 to make a one-piece single composite bearing.
  • This embodiment is easy to use, easy to handle, and does not require an outer ring spacer, and is thus advantageous from the cost viewpoint and because it allows size reductions in the diametrical direction. Also, assembly precision is high.
  • a single composite bearing shown in FIG 7 has a structure in which the single composite bearing and the inclination suppression gap g are established on the inner ring 1 side.
  • Sintered, oil-impregnated bearing 4 is combined with a single row ball bearing formed by inner ring 1, outer ring 2, ball 3 and retainer 5.
  • Sintered, oil-impregnated bearing 4 is press fitted or bonded onto the inner diameter part G of outer ring 2 to form a fixed structure which maintains inclination suppression gap g with the dimensions A and B on the inner ring side.
  • sintered, oil-impregnated bearing 4 is fixed together with outer ring 2 to make a one-piece single composite bearing, with the outer diameter of inner ring 1 and the inner diameter of outer ring 2 both processed to standard bearing dimensions.
  • This embodiment is easy to use, easy to handle, does not require an outer ring spacer or outer ring step processing, and is thus most advantageous from the cost viewpoint and because it allows size reductions in the diametrical direction. Also, assembly precision is high.
  • a single composite bearing comprises an inner ring 1, having a width L of the size necessary to restrain the inclination of the axis within the permitted range, and an outer ring 2, having a width which is half the width of the above mentioned width L, which is mounted above the outside half of inner ring 1 and separated from inner ring 1 by a gap.
  • a ball 3 is fitted into this gap between the rings and rests in grooves made in each ring. The ball 3 is prevented from escaping from the groove by retainer 5.
  • Inner ring 1 has an external form which is superfinished to high precision in one piece and contains the ball groove described above.
  • the outside of outer ring 2 is press fitted into outer ring sleeve 6, which is made of metal having a cylindrical form of width L.
  • Sintered, oil-impregnated bearing 7 is arranged in the space formed by the inner parts of outer ring 2, ball 3 and retainer 5. As shown in FIG 2, this sintered, oil-impregnated bearing 7 has an outer diameter which is smaller than the inner diameter of outer ring sleeve 6, and an inner diameter of the same size as the outer diameter of inner ring 1. Because of this, sintered, oil-impregnated bearing 7 is press fitted firmly to the outer side of inner ring 1 and forms a small gap g with the inner peripheral face of outer ring 2. This inclination suppression gap g, in order to prevent the inclination from exceeding the permitted range, is determined by the dimensions C and D shown in FIG 2, and accordingly extremely high precision processing is required.
  • FIGS 4, 6 and 8 show basically similar structures to the above, in which a single composite bearing has an inclination suppression gap g formed on the inner ring 1 side. These structures will be described in detail below.
  • the inclination suppression gap g is established with outer ring 2.
  • Outer ring 2 is assembled by bonding or press fitting to inner diameter E of the opposing part, thus forming inclination suppression gap g with inner diameter E of the opposing part.
  • This composite bearing structure as shown in FIGS 3 and 4 has the advantage of allowing the diametrical dimension to be reduced.
  • the inclination suppression gap g is established with the side of outer ring 2.
  • outer ring 2 has a processed stepped section with large diameter F, and sintered, oil-impregnated bearing 7 is press fitted or bonded onto inner ring 1 to form a structure which maintains inclination suppression gap g with this stepped large diameter part F and also establishes gap S with the edge side of the outer ring.
  • sintered, oil-impregnated bearing 7 is fixed together with inner ring 1 to make a one-piece single composite bearing.
  • This embodiment is easy to use, easy to handle, and does not require an outer ring spacer, and is thus advantageous from the cost viewpoint and because it allows size reductions in the diametrical direction. Also, assembly precision is high.
  • the inclination suppression gap g is established with the side of outer ring 2.
  • sintered, oil-impregnated bearing 7 is fixed together with inner ring 1 to make a one-piece single composite bearing, with the outer diameter of inner ring 1 and the inner diameter of outer ring 2 both processed to standard bearing dimensions.
  • This structure is easy to use, easy to handle, does not require an outer ring spacer or outer ring step processing, and is thus most advantageous from the cost viewpoint and because it allows size reductions in the diametrical direction. Also, assembly precision is high.
  • a double composite bearing comprises an inner ring 1, having a width L of the size necessary to restrain the inclination of the axis within the permitted range, and an outer ring 2, having a width which is the same as the above mentioned width L, which is mounted above the outside of inner ring 1 and separated from inner ring 1 by a gap.
  • a ball 3 is fitted into the central space between the two rings and rests in a groove in the outside of inner ring 1 and a groove in the inside of outer ring 2. The ball 3 is prevented from escaping from the ball groove by retainers 5.
  • Inner ring 1 is super finished in one piece to high precision in a shape having the ball groove described above.
  • Half-sintered oil-impregnated bearings 8 and 9, each having width I, are fitted into the space between inner ring 1 and outer ring 2 on each side of ball 3.
  • the outer diameters of half-sintered oil-impregnated bearings 8 and 9 are the same as the inner diameter of outer ring 2, and their inner diameters are slightly larger than the inner diameter of inner ring 1. Because of this, half-sintered, oil-impregnated bearings 8 and 9 are press fitted firmly to the inner side of outer ring 2 and form a small gap g with the peripheral face of inner ring 1.
  • This inclination suppression gap g in order to prevent the inclination from exceeding the permitted range, is determined by the dimensions A and B shown in FIG 9, and accordingly extremely high precision processing is required.
  • FIGS 11, 13 and 15 show basically similar structures to the above, in which a double composite bearing has an inclination suppression gap g formed on the inner ring 1 side. These structures will be described in detail below.
  • a double composite bearing shown in FIG 11 has a structure in which the inclination suppression gap g is established on the inner ring 1 side.
  • the opposing parts may be freely designed as regards shape, and can be directly assembled together with the opposing parts with no need for an outer sleeve ring 6. This has the advantage of allowing the diametrical dimension to be reduced.
  • a double composite bearing shown in FIG 13 has a structure in which the inclination suppression gap g is established on the inner ring 1 side.
  • a double composite bearing shown in FIG 15 has a structure in which the inclination suppression gap g is established on the inner ring 1 side.
  • a double composite bearing comprises an inner ring 1, having a width L of the size necessary to restrain the inclination of the axis within the permitted range, and an outer ring 2, having a width which is the same as the above mentioned width L, which is mounted above the outside of inner ring 1 and separated from inner ring 1 by a gap.
  • a ball 3 is fitted into the central space between the two rings and rests in a groove in the outside of inner ring 1 and a groove in the inside of outer ring 2. The ball 3 is prevented from escaping from the ball groove by retainers 5.
  • Inner ring 1 is super finished in one piece to high precision in a shape having the ball groove described above.
  • Half-sintered oil-impregnated bearings 10 and 11, each having width I, are fitted into the space between inner ring 1 and outer ring 2 on each side of ball 3.
  • the outer diameters of half-sintered oil-impregnated bearings 10 and 11 are slightly smaller than the inner diameter of outer ring 2, and their inner diameters are the same as the outer diameter of inner ring 1. Because of this, half-sintered, oil-impregnated bearings 10 and 11 are press fitted firmly to the outer side of inner ring 1 and form a small gap g with the inner peripheral face of outer ring 2.
  • This inclination suppression gap g in order to prevent the inclination from exceeding the permitted range, is determined by the dimensions C and G shown in FIG 10, and accordingly extremely high precision processing is required.
  • outer ring 2 side or inner ring 1 side begins to incline, part of one surface C of half-sintered, oil-impregnated bearings 10 and 11 will contact surface G of outer ring 2 and prevent any further inclination of the axis from occurring.
  • the size of the inclination of the axis can be determined by the size of inclination suppression gap g.
  • FIGS 12, 14 and 16 show basically similar structures to the above, in which a double composite bearing has an inclination suppression gap g formed on the outer ring 2 side. These structures will be described in detail below.
  • a double composite bearing shown in FIG 12 has a structure in which the inclination suppression gap g is established on the outer ring 2 side.
  • the assembly is formed as a single piece unlike the set shown in the example of FIG 14, and so both handling and assembly are easy.
  • the opposing parts may be freely designed as regards shape, and can be directly assembled together with the opposing parts with no need for an outer sleeve ring. This has the advantage of allowing the diametrical dimension to be made more compact.
  • a double composite bearing shown in FIG 14 has a structure in which the inclination suppression gap g is established on the outer ring side.
  • Sintered, oil-impregnated bearings 10 and 11, processed to the dimensions outer diameter C, inner diameter B and width I, are press fitted or bonded onto the outer diameter part of inner ring 1 and mounted, so as to preserve a gap S, on either side of outer ring 2 of the single row ball bearing formed by inner ring 1, outer ring 2, ball 3 and retainer 5, thus forming a structure which establishes inclination suppression gap g with outer ring sleeve 6.
  • the outer diameter dimension of the double composite bearing becomes large, but its one-piece construction offers the advantages of easy handling and assembly.
  • a double composite bearing shown in FIG 16 has a structure in which the inclination suppression gap g is established on the outer ring 2 side.
  • inner ring 2 as a rotating and stopping axis with no hollow spaces
  • the present invention provides a structure using one single row ball bearing with 1 ball (the smallest unit which can be used in a ball bearing), which, in order to solve the problem of inclination and vibration in the inner and outer rings, uses a sintered, oil-impregnated bearing with the objective of reducing inclination, where an inner or an outer ring of a single row ball bearing is mounted either on one side or on both sides, in a structure which reduces inclined rotation, and thus provides stable rotational support to the same extent as conventional ball bearings which require a minimum of 2 balls, and in which the bearing can be made thin in the direction of rotational support, and which, because only one ball bearing is required, can be made more inexpensively than conventional bearing structures.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Rolling Contact Bearings (AREA)

Claims (5)

  1. Kombiniertes Lager mit einem einreihigen Kugellager und einem zylindrischen Lager, aufweisend:
    einen inneren Ring (1) und einen äußeren Ring (2) des Reihenkugellagers, die koaxial mit einem Abstand zwischen sich angeordnet sind;
    zwischen Kugelrillen des inneren Rings und des äußeren Rings angeordnete Kugeln (3);
    gekennzeichnet durch
    ein zylindrisches Gleitlager (4, 7), das auf dem einen der beiden Ringe (1, 2) montiert ist und von dem anderen Ring durch einen Spalt (g) beabstandet und neben dem Kugellager angeordnet ist, um die Neigung des inneren Rings und des äußeren Rings des Kugellagers relativ zueinander zu verringern.
  2. Kombiniertes Lager nach Anspruch 1, bei dem die Kugelrille des inneren oder äußeren Rings (1, 2) auf einem Lagerteil ausgebildet und der Spalt in dem zylindrischen Gleitlager (4) zwischen einer zylindrischen Gleitlagerfläche und einer Fläche des Lagerteils gebildet ist.
  3. Kombiniertes Lager nach Anspruch 1, bei dem das zylindrische Gleitlager (4, 7) einen inneren Ring und einen äußeren Ring aufweist und der Spalt zwischen dem inneren Ring und dem äußeren Ring gebildet ist.
  4. Kombiniertes Lager nach Anspruch 1, bei dem das zylindrische Gleitlager (4, 7) auf der einen Seite des Kugellagers angeordnet ist.
  5. Kombiniertes Lager nach Anspruch 1, bei dem (8, 9) auf beiden Seiten des Kugellagers zylindrische Gleitlager angeordnet sind.
EP99301563A 1998-03-02 1999-03-02 Kombiniertes Lager Expired - Lifetime EP0940592B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP04911398A JP4099259B2 (ja) 1998-03-02 1998-03-02 複合軸受け
JP4911398 1998-03-02

Publications (2)

Publication Number Publication Date
EP0940592A1 EP0940592A1 (de) 1999-09-08
EP0940592B1 true EP0940592B1 (de) 2005-09-07

Family

ID=12822021

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99301563A Expired - Lifetime EP0940592B1 (de) 1998-03-02 1999-03-02 Kombiniertes Lager

Country Status (4)

Country Link
US (1) US6176620B1 (de)
EP (1) EP0940592B1 (de)
JP (1) JP4099259B2 (de)
DE (1) DE69927078T2 (de)

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DE10256086A1 (de) * 2002-11-29 2004-06-17 Leybold Vakuum Gmbh Kugellager und mit einem Lager dieser Art ausgerüstete Vakuumpumpe
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CA2532414C (en) 2003-07-12 2017-03-14 Accelr8 Technology Corporation Sensitive and rapid biodetection
DE10344804B4 (de) * 2003-09-26 2006-11-30 Aktiebolaget Skf Schwenklagerung
DE102005032283B3 (de) * 2005-07-11 2007-01-04 Meta Motoren- Und Energie-Technik Gmbh Kombiniertes Wälz- und Gleitlager
JP4668160B2 (ja) * 2006-11-09 2011-04-13 株式会社森精機製作所 軸受ユニット及び該軸受ユニットを備えた工作機械の主軸装置
US8459872B2 (en) * 2008-10-10 2013-06-11 General Electric Company Bearing with alternative load path for extreme loads
US10254204B2 (en) 2011-03-07 2019-04-09 Accelerate Diagnostics, Inc. Membrane-assisted purification
EP2683831B1 (de) 2011-03-07 2015-09-23 Accelerate Diagnostics, Inc. Schnelle zellreinigungssysteme
US8794847B2 (en) * 2011-09-14 2014-08-05 Aktiebolaget Skf Bearing assembly with axial retainer
CN102500774A (zh) * 2011-12-26 2012-06-20 东北大学 一种数控刀架三联齿盘定位结构
US8678655B1 (en) * 2012-04-11 2014-03-25 The United States Of America As Represented By The Secretary Of The Army Reinforced slewing bearing
US9677109B2 (en) 2013-03-15 2017-06-13 Accelerate Diagnostics, Inc. Rapid determination of microbial growth and antimicrobial susceptibility
US9494190B2 (en) * 2015-02-12 2016-11-15 Simmonds Precision Products, Inc Bearing assembly with overload protection
US10023895B2 (en) 2015-03-30 2018-07-17 Accelerate Diagnostics, Inc. Instrument and system for rapid microogranism identification and antimicrobial agent susceptibility testing
US10253355B2 (en) 2015-03-30 2019-04-09 Accelerate Diagnostics, Inc. Instrument and system for rapid microorganism identification and antimicrobial agent susceptibility testing
JP6379079B2 (ja) 2015-10-01 2018-08-22 透一 野渡 ラジアルころ軸受
DE202017101865U1 (de) * 2017-03-30 2018-07-03 Rollax Gmbh & Co. Kg Federbeinlager
JP6933007B2 (ja) * 2017-06-09 2021-09-08 株式会社ジェイテクト タッチダウン軸受及びタッチダウン軸受の製造方法
DE102018131102A1 (de) * 2018-12-06 2019-12-19 Schaeffler Technologies AG & Co. KG Verfahren zur Schwingungsdämpfung in einem Kraftfahrzeuggetriebe
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USRE28625E (en) 1970-08-03 1975-11-25 Rock drill with increased bearing life
DE2224111C3 (de) 1972-05-17 1975-07-03 Reich + Co Mellrichstadt, 8744 Mellrichstadt Laufrolle mit einem zapfenförmigen Lagerteil und einem Doppel-T-förmigen Radkörper aus Kunststoff
US4226484A (en) * 1978-12-20 1980-10-07 Hughes Aircraft Company Bearing retainer
US4309063A (en) * 1980-06-02 1982-01-05 C. L. Frost & Son, Inc. Bearing seal
US4394091A (en) * 1981-10-09 1983-07-19 General Motors Corporation Air bearing and antifriction bearing assembly
JPH0135549Y2 (de) * 1984-09-12 1989-10-30
JPS6165847U (de) * 1984-10-02 1986-05-06
JPS61114962U (de) * 1984-12-28 1986-07-21
JPH0535214Y2 (de) * 1988-03-31 1993-09-07
JPH0535213Y2 (de) * 1988-03-31 1993-09-07
JP2870057B2 (ja) * 1989-11-07 1999-03-10 日本精工株式会社 動圧軸受装置
JPH0756592Y2 (ja) * 1990-03-09 1995-12-25 株式会社三協精機製作所 スピンドルモーター
JPH0497450U (de) * 1991-01-17 1992-08-24
JP2555374Y2 (ja) * 1992-02-04 1997-11-19 群馬日本電気株式会社 複合軸受
JP2510374B2 (ja) * 1992-04-10 1996-06-26 大同メタル工業株式会社 転動子を有する滑り・転がり兼用型軸受
JPH09151939A (ja) * 1995-09-26 1997-06-10 Nippon Seiko Kk 軸受装置
JPH09119428A (ja) * 1995-10-24 1997-05-06 Nippon Seiko Kk 動圧軸受
US5642944A (en) * 1996-03-06 1997-07-01 W. L. Dublin, Jr. Auxiliary bearing system
JPH09317758A (ja) * 1996-05-31 1997-12-09 Nippon Seiko Kk 軸受装置
JPH1037952A (ja) * 1996-07-18 1998-02-13 Shuhei Takasu 複合軸受け
JPH1064002A (ja) 1996-08-19 1998-03-06 Hitachi Ltd 回転磁気ヘッド装置

Also Published As

Publication number Publication date
DE69927078T2 (de) 2006-01-19
EP0940592A1 (de) 1999-09-08
DE69927078D1 (de) 2005-10-13
JP4099259B2 (ja) 2008-06-11
US6176620B1 (en) 2001-01-23
JPH11247850A (ja) 1999-09-14

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